WO1997023409A1 - Treuil - Google Patents

Treuil Download PDF

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Publication number
WO1997023409A1
WO1997023409A1 PCT/CA1996/000855 CA9600855W WO9723409A1 WO 1997023409 A1 WO1997023409 A1 WO 1997023409A1 CA 9600855 W CA9600855 W CA 9600855W WO 9723409 A1 WO9723409 A1 WO 9723409A1
Authority
WO
WIPO (PCT)
Prior art keywords
winch
brake
cable drum
operatively connected
gear
Prior art date
Application number
PCT/CA1996/000855
Other languages
English (en)
Inventor
Jeffrey Morfitt
Barrie Freeke
Original Assignee
Seascape Systems Limited
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Seascape Systems Limited filed Critical Seascape Systems Limited
Priority to CA002241113A priority Critical patent/CA2241113C/fr
Priority to AU10900/97A priority patent/AU1090097A/en
Priority to GB9813222A priority patent/GB2329885B/en
Publication of WO1997023409A1 publication Critical patent/WO1997023409A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/02—Driving gear
    • B66D1/14—Power transmissions between power sources and drums or barrels
    • B66D1/22—Planetary or differential gearings, i.e. with planet gears having movable axes of rotation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63B—SHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING 
    • B63B23/00—Equipment for handling lifeboats or the like
    • B63B23/40—Use of lowering or hoisting gear
    • B63B23/48—Use of lowering or hoisting gear using winches for boat handling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
    • B66D5/026—Fluid-resistance brakes

Definitions

  • This invention relates to winches.
  • One application of the winches of the invention is in lowering evacuation craft from offshore drilling platforms, but the winches are in no way limited to that application.
  • One such system developed by the present applicant is based on an arrangement in which an elongated deployment arm is mounted at the side of a platform with the totally enclosed motor propelled survival craft (TEMPSC) supported at the end of the deployment arm.
  • TEMPSC totally enclosed motor propelled survival craft
  • the winch must fulfil a number of stringent design criteria. These include the fundamental requirement that the winch be capable of deploying the TEMPSC in a situation where there is an electrical power outage on the platform. The launch must obviously be at an acceptable low rate of speed and so a significant amount of energy must be dissipated by the winch. Furthermore, the winch must then be capable of recovering the TEMPSC and restoring it to the ready position. This last function is of particular importance for test pu oses.
  • the winch In addition to the operational requirements, the winch must be capable of operating in a hostile environment and must remain in top operating condition with minimum maintenance. It is against this background that the present invention arises.
  • FIGURE 1 illustrates an evacuation system of which the position of the major components is shown
  • FIGURE 2 is a front view of a winch according to the mvention
  • FIGURE 3 is a rear view of a winch according to the invention.
  • FIGURE 4 is a section illustrating a winch assembly according to the invention.
  • FIGURE 5 is a section illustrating a part of the winch assembly of FIGURE 4.
  • FIGURE 6 is a section showing a band brake mechanism for use in a winch according to the invention.
  • FIGURE 1 illustrates the general layout of an evacuation system for an offshore platform in association with which the winch of the present invention may be used.
  • a deployment arm 2 is rotatably mounted at 4 on the support structure of platform 6.
  • a lifeboat (TEMPSC) 8 is supported adjacent the end of arm 2. Deployment and retrieval of arm 2 are controlled by the winch 10 by means of cable 11.
  • FIGURES 2 and 3 illustrate the general arrangement of components of a winch 10 according to the invention. These figures illustrate in a preferred embodiment the relative position of cable drum 12, motor housing 14 and fall arrestor housing 16. Also shown is a brake actuator lever
  • motor housing 14 contains a motor 20 connected through a motor output shaft 22 to a gear reducer 24 within gear box 26.
  • Motor 20, motor output shaft 22 and gear reducer 24 are conventional and are not illustrated.
  • a final motor output shaft 28 extends at 90° and is fixed to a main cable drum shaft 30.
  • the sole function of the motor is to operate the winch in a retrieval mode for retrieving the deployment arm 2. This may occur after a practice drill or where an emergency situation no longer exists so that personnel may immediately return to the platform.
  • the motor is thus preferably provided with a conventional backstop or spragg-type clutch and a friction brake to ensure that the motor cannot drive the winch in a deployment mode to lower deployment arm 2, nor can the winch drum drive the motor in reverse.
  • gear reduction group 32 comprises a planetary gear system which most preferably consists of four stages.
  • the gear reduction provided by this system is preferably about 200:1.
  • the winch operates as follows. Sun gear 34 of first stage 36 is fixed on shaft 30 and rotates with that shaft. In the retrieval mode the planet gear carrier 38 of first stage 36 is held against rotation by brake means 40 to be discussed in detail later. Therefore, when shaft 30 is rotated by motor 20, the internal gear 42 of first stage 36 is caused to rotate by shaft 30. Internal gear 42 of first stage 36 is connected at spline 44 to sun gear 46 of second stage 48. Sun gear 46 is thus caused by internal gear 42 to rotate.
  • Planet gear carrier 64 of second stage 48 is connected through spline 66 to sun gear 68 of third stage 52. Sun gear 68 is thus caused to rotate with planet gear carrier 64. Therefore, since internal gear 50 is fixed, sun gear 68 acting through planet gear 70 of third stage 52 causes planet gear carrier 72 of third stage 52 to rotate.
  • Planet gear carrier 72 of third stage 52 is connected by spline 74 to sun gear 76 of fourth stage 56. Since planet gear carrier 54 of fourth stage 56 is fixed to end flange 58, sun gear 76 acting through planet gear 78 of fourth stage 56 causes internal gear 80 of fourth stage 56 to rotate. Internal gear 80 is fixed as generally illustrated at 82 to cable drum 12. Thus, cable drum 12 is caused to rotate to take up cable 11 to retrieve the deployment arm 2. To let out cable to lower deployment arm 2, the same gear reduction group 32 is utilized. However, since under no circumstances can the main shaft 30 rotate in the reverse direction, because of the backstop on motor 20, the interaction of the planetary gear system members in first stage 36 is altered. In the retrieval mode planet gear carrier 38 was held against rotation by brake means 40.
  • brake means 40 In the deployment mode, brake means 40 is released, so that planet gear carrier 38 is free to rotate. Since cable drum 12 is, in the ready mode, always loaded by the deployment arm 2 and the TEMPSC 8, drum 12 is always biased to rotate. Accordingly, once brake means 40 is released to allow planet gear carrier 38 to rotate relative to shaft 30, the weight of the TEMPSC 8 and the deployment arm 2 will immediately initiate descent.
  • Brake means 40 will be discussed in detail later but for present purposes it is noted that planet gear carrier 38 of first stage 36 is fixed to a brake shaft 84 with which a brake drum 86 rotates.
  • the brake per se is preferably in the form of brake band 88 operatively associated with brake drum 86.
  • brake band 88 is released from brake drum 86, thus freeing planet gear carrier 38 to rotate and to rotate brake shaft 84.
  • Fall arrestor 90 operates as follows. Brake shaft 84 is provided with a gear 92 which is fixed to and rotates with brake shaft 84. Thus, when the brake band 88 is released so that shaft 84 rotates, gear 92 also rotates. Gear 92 is operatively connected to gear 94 which is fixed to pump shaft 96. Pump shaft 96 is in turn connected to drive hydraulic pump 98. In one preferred embodiment a series of gears 94 are arranged to be driven by gear 92 to in turn drive a series of hydraulic pumps 98. In one preferred case two such pumps are utilized.
  • housing 100 comprises a reservoir which is maintained filled with hydraulic fluid and in which pump 98 is immersed. Therefore, when pump 98 is driven by pump shaft 96, hydraulic fluid is pumped through pump outlet 102 into passage 104. Hydraulic fluid then flows through a flow restrictor 106 into a second passage 108 and hence into brake housing 110. Hydraulic fluid can then circulate through passage 112 back into the reservoir formed by housing 100.
  • the flow restrictor is chosen to permit hydraulic fluid to flow past at a rate which will by back pressure slow the pump 98.
  • pump shaft 96, and, through gears 94 and 92, brake shaft 84 will also be slowed. Accordingly, rotation of planet gear carrier 54 will be correspondingly slowed. Therefore, the rate of rotation of cable drum 12 at the other end of gear reduction group 32 will also be slowed.
  • the size of the flow restrictor will be chosen to yield the design speed of deployment.
  • brake means 40 comprises, as indicated, a brake drum 86 associated with brake shaft 84 and having brake band 88 operating against outer surface 114 of brake drum 86.
  • Braking is applied to the system by increasing the tension on brake band 88 to cause frictional engagement with outer surface 114 of brake drum 86.
  • the brake is applied by pulling the end 116 of brake band 88 to the left as shown in FIGURE 6.
  • the brake must be capable of being released remotely from within the TEMPSC by simple mechanical means.
  • personnel will in an evacuation situation board the TEMPSC, seal the hatches and then release the brake.
  • One manner of accomplishing this is illustrated.
  • End 116 of brake band 88 is secured through mechanism 117 in an upper section 118 of lever 120.
  • Lever 120 is pivoted about an axis through point 122.
  • a second mechanism 124 is secured within a second section 126 of lever 120.
  • the rod 128 extending through housing 130 is connected to end 132 of mechanism 124 by an eccentric 134.
  • mechanism 124 to be raised or lowered in FIGURE 6 and thus through lever 120 to release or apply tension to brake band 88.
  • the brake actuator lever 18 is fixed to outer end 138 of rod 128. Thus, manipulation of brake actuator lever 18 will, through the mechanism described, apply or release the brake.
  • One manner of maintaining the brake in the applied condition utilizes a series of weight plates 140 attached to brake actuator lever 18.
  • Brake actuator lever 18 is fixed to the brake mechanism such that when the brake is in the applied condition, the brake actuator lever 18 will be held by the weights to one side of top dead center point in the path of rotation of lever 18. In order to release the brake, and to ensure that the brake remains in the released condition, brake actuator lever 18 is moved through top dead center so that the weight plates 140 then maintain the mechanism in the brake released condition.
  • brake actuator lever through top dead center to release the brake can readily be achieved by, for example, a cable extending from the TEMPSC (not shown). While one embodiment of an arrangement of brake actuator lever 18 has been illustrated, others are possible and some preferable. For example, one highly preferred arrangement (not illustrated), would utilize the weight plates 140 to remove rather than apply the brake. A simple stop arrangement would hold the weights against releasing the brake until a cable pull from the TEMPSC releases the stop. The weights would then fall to release the brake.
  • the shuttle mechanism 142 In order to facilitate retrieval of the deployment arm 2 where that is required and to prevent damage to either the deployment arm or to the platform support structure, it is advantageous to limit the amount of cable which the winch can let out to that which is sufficient to properly launch the TEMPSC.
  • the shuttle mechanism 142 has been provided. This mechanism functions as follows. The gear 144 is fixed to the end 146 of drum 12 to rotate with drum 12. Gear 144 then drives through a gear train consisting of gears 148 and 150 to bevel gear 152.
  • Bevel gear 152 then drives a companion gear 154 mounted on screw shaft 156.
  • the shuttle 158 is mounted on the screw shaft 156 and travels back and forth along shaft 156 as drum rotation causes rotation of shaft 156 through the gear train just described.
  • the lever 120 is caused to rotate about its pivot axis to thereby reapply brake band 88.
  • the number of rotations of drum 12 required to move shuttle 158 across shaft 156 to cause reapplication of the brake is chosen to coincide with the desired amount of cable having been let out from drum 12.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Emergency Lowering Means (AREA)
  • Jib Cranes (AREA)

Abstract

Cette invention concerne un treuil nouveau et utile (10), lequel comprend les éléments suivants: un tambour de câble (12); un moteur (20) connecté de manière fonctionnelle au tambour de câble (12) et entraînant celui-ci; un arrêtoir de garant (90) connecté de manière fonctionnelle au tambour de câble (12) et ne nécessitant aucune entrée électrique; et, enfin, un groupe d'engrenages réducteurs (32) par l'intermédiaire duquel le moteur (20) et l'arrêtoir de garant (90) sont connectés de manière fonctionnelle au tambour de câble (12).
PCT/CA1996/000855 1995-12-21 1996-12-20 Treuil WO1997023409A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CA002241113A CA2241113C (fr) 1995-12-21 1996-12-20 Treuil
AU10900/97A AU1090097A (en) 1995-12-21 1996-12-20 Winch
GB9813222A GB2329885B (en) 1995-12-21 1996-12-20 Winch

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US08/576,683 1995-12-21
US08/576,683 US5860635A (en) 1995-12-21 1995-12-21 Winch having hydraulic speed control and planetary gear system

Publications (1)

Publication Number Publication Date
WO1997023409A1 true WO1997023409A1 (fr) 1997-07-03

Family

ID=24305522

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA1996/000855 WO1997023409A1 (fr) 1995-12-21 1996-12-20 Treuil

Country Status (5)

Country Link
US (1) US5860635A (fr)
AU (1) AU1090097A (fr)
CA (1) CA2241113C (fr)
GB (1) GB2329885B (fr)
WO (1) WO1997023409A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998008569A1 (fr) * 1996-08-30 1998-03-05 Law, Yiu, Kwan Appareil de securite et son procede
WO2013064564A1 (fr) * 2011-11-01 2013-05-10 Nadiro A/S Système hydraulique refroidi
WO2021120384A1 (fr) * 2019-12-18 2021-06-24 永州市金蚂蚁新能源机械有限公司 Treuil de frein à disque mécanique portatif

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JP2001506570A (ja) * 1996-11-19 2001-05-22 コスタンチノビッヒ カムルジャック、アレクサンダー 車両の伝達歯車装置により駆動されるホイスト
US6631816B1 (en) 1999-03-18 2003-10-14 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Hoist
JP2001072358A (ja) * 1999-07-02 2001-03-21 Teijin Seiki Co Ltd エレベータ用巻上げ装置
DE10011187A1 (de) * 2000-03-08 2001-09-13 Flender A F & Co Getriebe für eine Tiefbohrlochpumpe
US6604731B2 (en) * 2001-11-12 2003-08-12 Warn Industries, Inc. Utility winch
US20050063857A1 (en) * 2003-09-23 2005-03-24 Alheidt Thomas A. Flush syringe having anti-reflux stopper
DE102004043592B3 (de) * 2004-09-09 2006-03-09 Demag Cranes & Components Gmbh Sicherheitsbremseinrichtung einer Wickeltrommel sowie Arbeitsverfahren zum Einschleifen der Sicherheitsbremse
US20080000735A1 (en) * 2006-06-29 2008-01-03 Shih Jyi Huang Braking device for a power winch
US7823864B2 (en) * 2006-08-17 2010-11-02 Yuzhi Xie Plane braking device for electric winches and electric winch
US7780146B2 (en) 2007-09-28 2010-08-24 D B Industries, Inc. Retrieval assembly
CN101381059B (zh) * 2008-10-29 2010-06-30 杭州天铭机电工具有限公司 绞车
US7789375B2 (en) * 2008-12-02 2010-09-07 Mojack Distributors, Llc Portable winch assembly actuated by auxiliary handheld torquing device
US20100239371A1 (en) * 2009-03-19 2010-09-23 Curtis Brown Boat lift
US8246010B2 (en) * 2009-08-13 2012-08-21 Hess Daniel L Fluid shear actuated hoist brake
CN101746687B (zh) * 2010-01-12 2011-11-30 杭州天铭机电工具有限公司 一种导绳装置
US8523147B2 (en) * 2010-11-09 2013-09-03 Ningbo Chima Winch Co., Ltd. Electric capstan
US9150391B2 (en) * 2012-03-30 2015-10-06 Harnischfeger Technologies, Inc. Hoist drive for mining machine
US9315364B2 (en) 2013-03-08 2016-04-19 Warn Industries, Inc. Remote winch clutch system
US9868619B2 (en) 2014-11-06 2018-01-16 Ramsey Winch Company Self-engaging clutch
EP3369692B1 (fr) * 2017-03-03 2021-10-27 Goodrich Corporation Chaîne cinematique et palan de sauvetage
US10634218B2 (en) * 2017-11-01 2020-04-28 David R. Hall Multiplying nested gearbox
CN109368525B (zh) * 2018-10-30 2020-08-07 姜启胜 安装有自动换挡的行星齿轮变速器的卷扬机
CN111533017B (zh) * 2020-05-16 2021-11-19 济宁元昇机电股份有限公司 一种具有自由下放功能的全液压绞车
CN115010031B (zh) * 2022-08-08 2022-10-25 河南华工实业集团有限公司 一种可防止快速放线的起重机卷筒

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FR1159283A (fr) * 1955-10-15 1958-06-25 Scheuchzer Fils Auguste Treuil
DE1812582A1 (de) * 1968-12-04 1970-06-18 Stahlberg Hans Joachim Abseilwinde
GB2087826A (en) * 1980-11-15 1982-06-03 Cameron Antony Duncan Controlled torque apparatus for cables
EP0176832A1 (fr) * 1984-09-20 1986-04-09 Paccar Inc. Système de levage à tension constante

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Publication number Priority date Publication date Assignee Title
US1843793A (en) * 1928-11-26 1932-02-02 Koehring Co Safety skip control device
US2246923A (en) * 1938-07-26 1941-06-24 Chicago Pneumatic Tool Co Brake for hoists
FR1159283A (fr) * 1955-10-15 1958-06-25 Scheuchzer Fils Auguste Treuil
DE1812582A1 (de) * 1968-12-04 1970-06-18 Stahlberg Hans Joachim Abseilwinde
GB2087826A (en) * 1980-11-15 1982-06-03 Cameron Antony Duncan Controlled torque apparatus for cables
EP0176832A1 (fr) * 1984-09-20 1986-04-09 Paccar Inc. Système de levage à tension constante

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998008569A1 (fr) * 1996-08-30 1998-03-05 Law, Yiu, Kwan Appareil de securite et son procede
WO2013064564A1 (fr) * 2011-11-01 2013-05-10 Nadiro A/S Système hydraulique refroidi
WO2021120384A1 (fr) * 2019-12-18 2021-06-24 永州市金蚂蚁新能源机械有限公司 Treuil de frein à disque mécanique portatif

Also Published As

Publication number Publication date
CA2241113A1 (fr) 1997-07-03
US5860635A (en) 1999-01-19
GB9813222D0 (en) 1998-08-19
GB2329885B (en) 1999-05-19
AU1090097A (en) 1997-07-17
CA2241113C (fr) 2005-08-23
GB2329885A (en) 1999-04-07

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